Pumping mechanism



Aug. 11, 1936. R. R. WITHERELL PUMPING MECHANISM Filed y 1-934 5 Sheets-Sheet l INVENTOR. ROBERT R. W/THf/fiflL BY W M A TTORNEYS.

Alig. II, 1936. R. R. WITHERELL 2,050,823

PUMPING MECHANISM Filed May 12, 1934 5 Shams-Sheet 2 BYX W M A TTORNE YS.

Aug. 11, 1936. R. R. WITHERELL PUMPING MECHANISM Filed May 12, 1934 5 Sheets-Sheet 5 INVENTOR. R055? T f? w/ 7/9 55 1-1 L BY M M ATTORNEYS.

Aug. 11, 1936. R. R. WITHERELL PUMPING MECHANISM Filed May 12, 1934 5 Sheets-Sheet 4 A TTORNEYS.

" BYA WR, M

R. R. WITHERELL 2,050,823

PUMPING MEQHANISM Filed May 12, 1934 5 Sheets-Sheet 5 INVEN ROBERT P. W/7 'H LL A TTORNE Y.

Patented Aug. 1 1, 1936 UNITED STATES PATET OFFIQE PUlVIPING MECHANISM Ill.

Application May 12, 1934; Serial No. 725,271-

3 Claims.

This invention relates to improvements in pumping mechanism and more particularly to the type of displacement pump employed for metering fluids.

While a particular application of this improved pumping mechanism is illustrated and described here, it is to be understood that its use is not limited to this particular application, as it will act in the same improved manner wherever used.

An example of the application of a displacement pump for feeding fluid fuel to a fluid fuelburning device is found in the patent granted to Walter W. Williams, No. 1,817,051, August 4, 1931. This patent discloses a metering pump that provides a constant flow of fluid fuel, irrespective of the viscosity of such fuel, from the source of supply to the burner nozzle.

It is an object of this invention to provide a metering pump of this type so constructed that it possesses a double function; namely, to act as a valve. in the fluid line to prevent seepage of the fuel through the pump when the burner mechanism is idle, and to deliver a constant flow offuel when the burner mechanism is in operation.

In the fluid fuel-burning mechanism including this invention, it is not necessary to provide a fluid: fuel valve in the connection between the pump and source of fluid supply, nor is it necessary to provide an automatic means for opening. and closing said valve upon the starting or cessation of operation of the burner mechanism.

With these and other objectsin view, reference is-made to the accompanying sheets of drawings, which illustrate a preferred form of this invention with the understanding that minor detail changes may be made without departing from the scope thereof.

In the drawings:

Figure lis a view in longitudinalvertical section taken through the pumping means for delivering fluid fuel in a fluid fuel-burning mechamsm;

Figure 2 is a fragmentary view in section taken 5:-:,on:the-1ine2-2, Figure 1, looking in the direction of the arrows and showing a fluid fuel pump.

Figure 3 is a view in horizontal section taken onthe line 3-3, Figure 1, looking in the directiorrof the arrows.

5.0. 3 Figure 4 is a view in transverse section taken on the line 44, Figure 1, looking in the direction of the arrows and-showing the means for adjusting the delivery of the metering pump with the piston shown in elevation.

Figure 5 is a-viewsimilar to Figure 4, showing a different position of the metering pump rotor.

Figure 6 is a view in transverse section taken on the line -t6, Figure 1, looking in the direction of the arrows and showing the intake ports of the meteringpump.

Figure 71s a similar view in section taken on the line 'I-1, Figure 1, looking inthe direction of the arrows and showing the discharge ports of the metering pump.

Figure 8 is a reduced view in transverse sectiontaken on the line B8, Figure 1, looking in the direction of the arrows, with parts shown in elevation.

Figure 9 is a fragmentary view similar to Figure 1, illustrating a modified form of this invention.

Figure 10 is a detail view in section taken on the line I0IIJ, Figure 9, looking in the direction of the arrows, with parts broken away.

Figure 11 is a view similar to Figure 10, taken on the line I I -I I, Figure 9.

The embodiment of this invention illustrated in Figure 1 shows an improved fluid fuel delivery mechanism of the general type disclosed in said Williams-Patent No. 1,817,051 and includes an oil pump casing I, and oil strainer casing 2, a metering pump casing 3, a delivery pump casing 4, mounted in the order named upon each other, and secured to the end bell 50f an electric motor, whereby said end bell forms one side of the delivery pump casing 4- and in such a manner has to surround a prolongation of the motor driving shaft 6. The casing I encloses a pump rotor I, the metering pump casing 3 encloses a metering pump rotor 8, and the delivery pump casing 3 encloses a delivery rotor 9, which delivery rotor is splined-or otherwise'flxed on the extension 6 of the motor driving shaft and the other rotors-are connected to each other by the shaft I0 of the pump rotor I, and the metering pump rotor is connected to the extension 6 of the motor driving shaft by the alignedconnecting shaft II.

The oil pump casing I is preferably secured to theoil strainer casing 2 by studs, not shown. The oil strainer casing 2' is provided with an oil'inlet passage I2 adapted to be connected to an oil supply pipe I3, the other end of which passage registers with a passage I2 in the pump casing I, which, in turn, opens into a cylindrical cavity I l-concentric with the axis of the motor shaft.

The cavity M is closed by a seat I5 for the oil pump rotor l. The oil pump is preferably of the type shown in the SperryPatent No. 1,622,816, March 29, 1927, and includes the member I6 havin'g-a rectangular opening and a frame ll-"mount ed in said opening and bearing against the seat l5. The seat I 5 of the oil pump is held immovable against the casing I by the shaft l8, one end of which is screw-threaded into the casing I and the other end enlarged to engage the working face of the seat l5. The enlarged end l9 acts as a bearing for the inner rectangular rotating piston 20 of the pump. The seat I5 is provided with inlet ports 2| extending therethrough from the cavity l4 and diametrically opposed outlet or discharge ports 22 leading from the pump through a passageway 23 in the pump casing registering with a passageway 24 formed in the wall of the strainer casing 2 opening into a chamber 25 at the top of said casing. The casing 2 encloses a cylindrical wire oil strainer 26 closed at the bottom and connected at the top to the chamber 25, whereby the fluid fuel is conveyed from the source of supply through pipe l3, passageways I2 and I2 Figure 3, inlet port 2|, through oil pump, discharge port 22, passages 23 and 24, Figure 1, and through the mesh of the strainer 26 to a space 21 provided in the casing 2 at the rear of the pump rotor I.

The rotor l of the oil pump is preferably formed integral with the shaft I and is mounted within a housing 28 preferably screw-threaded at one end into the casing l with that end recessed and provided with a spring-pressed bearing ring 29 engaging the rear of the rotor to hold the working face of the rotor in engagement with the enlarged end |9 of the shaft l8 and the members l6, l1 and 28 in engagement with the working face of the seat |5. The other end of the housing is extended to pass through an aperture in the wall of the oil strainer casing 2 which communicates with the space 27 therein. The upper side of the housing 28 which passes through and beyond the oil strainer casing 2 is provided with a groove or duct 36, the purpose of which will hereinafter be described.

The metering pump casing 3 includes a housing 3| containing a cylindrical chamber 32 concentric with the axis of the motorshaft 6 within which are mounted two spaced-apart cylindrical bearing rings 33 for the cylindrical metering pump rotor 8, one fiat face of which is keyed upon the end of the pump rotor shaft l0 extending beyond the casing 28 and the other fiat face is keyed to one end of the connecting shaft II, the other end of which is keyed to the projection of the motor shaft 6. One side of the housing 3| is closed by a central recessed member 34 interposed between the oil strainer casing 2 and portion 3| of the metering pump casing, which member is axially perforated to snugly receive the extension of the housing 28 which enters into the recess 35 of said member. The opposite side of the casing or member 3| of the metering pump is closed by a member 36 having a central circular opening 31 therethrough concentric with, and of greater diameter than, the connecting shaft H, which shaft passes through said opening to engage the end of the projection 6 of the rotor shaft. The member 36 is recessed upon the side of the metering pump rotor to form a chamber 38 similar to the oppositely disposed chamber 35.

The oppositely disposed flat faces of the rotor 8 rotate between bearing discs 39 and 46, which are held in engagement with the rotor by coil springs 4| and 42 having ends in engagement with the members 34 and 36 respectively. The rear sides margining the peripheries of the re- :spective bearing discs 39 and 40 are each connected to a metallic bellows 43, the opposite ends of the respective bellows being connected to diaphragms 44 and 45 which are countersunk within the chambers 35 and 38 to receive the said bellows, and the margins of the diaphragms extend throughout the housing 3| of the metering pump casing and are secured thereto by the members 34 and 36.

The metering pump includes the provision of a pump cylinder 46 in the rotor 8 with its axis passing through the axis of the rotor, opening through the rotor circumference at one end and closed at'the other, which closed end is in communication with the inlet and discharge ports 41 and 48 which are preferably arranged at an angle to each other, as shown in Figure 1. A spring-pressed piston or plunger 49 is mounted for reciprocation within the cylinder 46 by engagement with a cylindrical surface 50 eccentric to the rotor 8 upon the interior of an adjustable ring mounted within the chamber 32. Therefore, the metering pump operates in the same manner as disclosed in the Walter W. Williams Patent No. 1,817,051. It is preferable to regulate the capacity of the metering pump by altering the movement of travel of the piston 49 by adjusting the eccentricity of the ring 5|. In order to adjust the eccentricity of the ring 5|, it is pivoted at one side upon a pivot pin 52 between the spaced-apart bearing rings 33 and is normally urged to rotate upwardly about said pivot by a spring 53 contained within one of the bearing rings 33 and extending between the outer circumference of said ring and the adjacent cylindrical wall of the chamber 32. The upper side of the member 3| is provided with a vertical radial extension 54 which mounts an adjusting screw 55 passing through adequate packing to enter Within the chamber 32 and contact the outer surface of the adjustable ring 5| whereby the eccentricity of the ring may be adjusted.

The opposite fiat surface of the rotor 8 and the contiguous surfaces of the bearing discs 39 and 46 are ground to form lapped joints with each other. The bearing disc 39 on the side adjacent the oil pump isprovided on one side of the vertical center with a series of closely adjacent intake ports 56 arranged on the arc of a circle concentric with the axis of the rotor 8 and adapted to successively registerwith the intake port 4! of the rotor as it wipes thereover. The oppositely disposed bearing disc 48 upon the opposite side of the rotor is provided with similarly arranged and oppositely disposed outlet ports 51 adapted to successively register with the discharge port 48 of the metering pump as the rotor wipes thereover, as clearly shown in Figures 6 and 7 on the drawings. vIt is seen that when any of the intake ports 56 are registering with the intake port 41 of the rotor, the discharge port 48 of the rotor will be closed by the lapped joint made by the rotor with the bearing disc 40; therefore, the oil passing through the strainer 26 and space 21, which passes through the duct 36 into the recess 35 and from there through the intake ports 56 in the bearing disc 39 and into the intake port 41, cannot seep between discharge port 48 of the metering pump should the rotor drical chamber eccentric to the rotor 9 mounted therein upon the extension 6 of the rotor shaft. The member 36 forms a closure upon one side of the chamber 48 and the other side is closed by the fiat surface of the end bell 5. The delivery rotor 9 is provided with a plurality of slots 59 parallel to the axis thereof, but arranged at one side thereof, which mount slidable vanes 69 which act as a seal in contacting the surface of the eccentric chamber 58 under the influence of centrifugal force when the rotor is in operation, as clearly shown in Figure 8. When the metering pump is in operation, the fluid fuel delivered through the discharge ports 51 in the bearing plate 40 passes through the opening 31 in 'the member 36 and through a port 6| opening into the chamber 58 where it is entrapped between two of the sliding vanes and thereafter delivered through a pipe 62 to the nozzle of the burner mechanism.

In the form shown in Figure 9, the pressure pump casing 4 and the metering pump casing 3 are connected in the same manner as shown in Figure 1. However, the strainer casing 2 and oil pump casing l have been omitted. The member 34 corresponding to the member 34 in Figure 1, is provided with a central port 34 and the end of the member 34* is shouldered for the reception of a casing, not shown, to be substituted for the oil pump in casing l, and the oil strainer casing 2, which casing forms a chamber communicating with the port 34 and with the source of oil supply. The bearing plate 99 is provided with intake ports 56 and is similar in construction with the bearing plate 39, Figure 1, but in this case may be imperforate and is held against the rotor 8 by the coil spring 4|. Packing rings 43 are substituted for the bellows 43 and disc 44 of Figure 1. The member 36 is substituted for the member 36 of Figure 1 and is provided on the side adjacent the metering pump rotor with a recess 38 to non-rotatably receive a block 40 to act in the same manner as the bearing plate 49 of Figure 1. The bearing plate 39 is provided with ports in the same manner as the bearing plate 39, as shown in Figures 1 and 6, and the block 40 is provided with ports 5! which correspond with the ports in the bearing plate 40, as shown in Figures 1 and 7.

The metering pump rotates between the bearing plate 39 and block 40* and forms lapped joints with the contacting surfaces thereof in the same manner as described in connection with Figure 1, and forms a seal between the source of oil supply and the pressure pump in the same manner as hereinbefore described.

What I claim is:

1. A pumping mechanism, comprising a casing, a rotor mounted for rotation within the casing, a reciprocable piston mounted within a chamber provided therefor in the rotor, cooperating means 5 within the casing to reciprocate the piston, ports within the rotor leading from the piston chamber through opposite ends of the rotor, non-rotatable bearing discs mounted within the casing bearing against the opposite ends of the rotor, ports in the bearing discs adapted to register alternately with the rotor ports whereby when one set of said ports is in connection with a rotor port the other rotor port is closed by the other disc, and said rotor being mounted for rotation within two spaced-apart annular bearings mounted within the casing, the cooperating means to reciprocate the piston including a spring for normally extending the piston, a guide ring normally engaged by the extended spring-pressed end of the 20 piston and pivotally mounted between the said spaced-apart rotor bearings, and means for adjusting the eccentricity of said guide ring to said rotor.

2. The structure of claim 1 wherein said ad- 25 justing means includes a spring mounted in the casing and normally bearing upon the exterior of the guide ring, and a set screw mounted on the other side of the casing adapted to engage the outer surface of the guide ring to rotate 30 the same about its pivot against the tension of the spring.

3. A pumping mechanism, comprising a casing,

a rotor mounted for rotation within the casing,

21. reciprocable piston mounted within a chamber 35 provided therefor in the rotor, cooperating means within the casing to reciprocate the piston, ports within the rotor leading from the piston chamber through opposite ends of the rotor, non-rotatable bearing discs mounted within the casing bearing against the opposite ends of the rotor, ports in the bearing discs adapted to register alternately with the rotor ports whereby when one set of said ports is in connection with a rotor portthe other rotor port is closed by the other disc, the opposite ends of the casing being provided with closures recessed on the inner side for the mounting of the bearing discs, with one closure provided with an inlet port and the other with a discharge port, metallic diaphragms interposed between said closures and said casing, and metallic bellows connected to the respective diaphragms and the respective bearing discs.

ROBERT R. WITHERELL. 55 

